Machine tool



July 29, 1941. cs. F.- BRYANT MACHINE TOOL l1 Sheets-Sheet l 1 Filed June 26, 1940 G. F. BRYANT July 29, 1941.

' MACHINE TOOL Filed Jilne 26, 1940 ll Sheets-Sheet 2 July 29, 1941. G. :1 BRYANT MACHINE TOOL Filed June 26, 1940 11 Sheets-Sheet s fzzlemfor." g oggef'flyazzt W M W4;

July 29, 1941. G. F. BRYANT MACHINE TOOL Filed June 26, 1940 11 SheetsSheet 4 29, 1941- G. F. BRYANT- I 2,251,034

MACHINE TOOL Filed Jul le 26, 1940 ll Sheets-Sheet 5 July 29, 1941. e. F. BRYANT MACHINE TOOL Filed June 26, l9 40 11 Sheets-Sheet 6 July 29, 1941. G. F. BRYANT 11 Sheets- Sheet '7 MACHINE TOOL Filed June 25 1940 fizz/6712507; ye 1 3 47210 li au $4., 65%,; m

July 29, 1941. G. F. BRYANT MACHINE TOOL 11 Sheets-Sheet 8 Filed June 26, 1940 e. F. BRY'ANT Jul 29, 1941.

MACHINE TOOL Filed June 26, 1940 11 Sheets-Sheet 9 July 29, 1941 v G. F. BRYANT MACHINE TOOL Filed June 26, 1940 Sheets-Sheet l0 1&5 0' .w' FF! 0 Y 192067220 B fieo geifir yaiuj Patented July 29, 1941 TENT OFFICE MACHINE TOOL George F. Bryant, Chica half to Lucien I. Ye

go, 111., assignor of oneomans, Chicago, Ill.

Application June 26, 1940, Serial No. 342,479

40 Claims.

The present invention pertains to machine tools and has been illustrated herein as incorporated in a machine tool especially adapted for shaping artillery shell blanks preparatory to turning and boring although those skilled in the art will readily perceive that a number of the features of the invention are of more or less general utility in machine tools.

One object of the invention is to provide a machine especially adapted to machine, at a high production rate, artillery shell blanks or the like in such manner as to form on them an integral rib or other chuck element suitable for use in transmitting the torsion loads on the blanks in subsequent turning or boring operations.

Another object of the invention is to provide a machine adapted to effect expeditiously and economically the end surfacing and drilling of generally cup-shaped metal blanks such as are used for artillery shells.

Another object is to provide a machine tool for performing a metal removing operation on generally tubular metal blanks and which is characterized particularly by the novel arrangement for routing and feeding the blanks through the machine in a more or less continuous stream with speedy and effectual manipulation of the same even when the blanks are quite heavy and bulky as in the case of forged steel blanks for artillery shells.

Another object is to provide in a machine tool of the turret type, a novel arrangement or organization of the parts to facilitate two-man operation, such that one workman stationed on one side of the machine can supervise loading and unloading of the blanks while a second workman on the other side of the turret looks after one or more machining or metal removing operations, the distribution of parts being such as to facilitate efficient operation of a number of elements by each man but without danger of interference between them.

Another object is to provide in a, turret type machine tool with a plurality of individually releasable work-holders on the turret, a novel arrangement for actuating the work-holders such that they can be individually released upon arrival at a desired station by suitable power means and yet such that no power supply connections to the revolving turret itself are required.

A more specific object is toprovide a machine tool of the character set forth in the last statement of object above and in which a novel arrangement of the work-holders is used, such that they may be individually revolved in carrying out certain machining operations despite the novel releasing mechanism noted.

Another object is to provide a turret type machine tool with a series of individually revoluble work-holders on it and having means for utilizing a single stationarily mounted drive for revolving successive ones of the work-holders at a predetermined station of the turret so that only one driver is required for the whole series of work-holders and even that one need not be mounted on the turret so that the necessity of providing a power supply to it on the moving turret is obviated.

Still another object is to provide a novel machine tool of the turret type such that successive workpieces on the turret can be machined at different stations and by different tools requiring, respectively, rigid clamping of the work and power driven rotation of the same as, for example, in milling a surface on the work anddrilling the same by revolving the work with the latter engaged with a non-rotatable drill bit.

A further object is to provide a machine tool having an element, such as a carriage, traversable between limit positions together with a novel drive arrangement therefor such as to insure precision location of the element in its respective limit positions.

The invention also resides in various improvements in the construction and organization of the work-handling mechanism in the machine tool by virtue of which the workpieces are handled swiftly and accurately with quite a simple mechanism.

Further objects and advantages of the invention. will become apparent as the following description proceeds, taken in connection With the accompanying drawings in which:

Figure 1 is a plan view of a machine embodying the invention.

Fig. 2 is a detail perspective view of a blank or workpiece of the type adapted to be machined by the apparatus of Fig. 1'.

Fig. 3 shows the blank after it is machined.

Fig. 4 is. a front elevation of the machine of Fig. 1.

Fig. 5 is an enlarged detail sectional view taken substantially along the line 55 in Fig. 4.

Fig. 6- is a sectional view along the line 6-6 in Fig. 5.

Fig. 7 is an end elevation of the machine taken from the right hand end as viewed in Fig. 4 but with the unloader removed.

Fig. 8 is an enlarged partial plan view of the Fig. 14 is an enlarged transverse sectional view taken substantially along the line I l-44 in Fig. 7

Fig. 15 is a vertical sectional view taken substantially along the line l5-l 5 in Fig. 14.

Fig. 16 is an enlarged fragmentary side elevation, partially in vertical section, of the turret and mandrels carried thereby.

Fig. 17 is a transverse sectional view along the line l'l-l'l in Fig. 16.

Fig. 18 is an enlarged fragmentary rear elevational view of the machine showing particularly the milling cutter drive mechanism.

Fig. 19 is a vertical sectional View taken substantially along the line Iii-l9 in Fig. 18.

Figs. 20 and 21 are, respectively, vertical and horizontal sections taken along the lines 292il and 2l-2l in Fig. 19.

Fig. 22 is an enlarged side elevation of the unloader mechanism.

Fig. 23 is a plan view of the unloader mechanism shown in Fig. 22.

Fig. 24 is a vertical sectional view taken substantially along the line 24-44 in Fig. 22.

While the invention is susceptible of various modifications and alternative constructions, I have shown in the drawings and will herein describe in detail the preferred embodiment, but it is to be understood that I do not thereby intend to limit the invention to the specific form disclosed, but intend to cover all modifications and alternative constructions falling within the spirit and scope of the invention as expressed in the appended claims.

The machine herein illustrated as an exemplification of my invention is especially adapted for the preparation for turning and boring of cupshaped forged steel blanks like I53 (Fig. 2) for artillery shells. The blanks IE! are initially forged in a shape like that of Fig. 2. Thereafter it is necessary to rough bore and turn them, taking one or more boring and turning cuts on their interiors and exteriors. Then the open end portions of the blanks are drawn into suitably pointed form and the shells finally finish machined. It has heretofore been the practice to chuck the blanks by exterior or interior frictional grip devices during the rough boring and turning operations noted. Such turning and boring of heavy workpieces, however, subjects the friction gripping elements'to tremendous stresses, so that slippage with consequent tool breakage and workpiece damage has been common. In the copending application Serial No. 342,436 filed June 26, 1940 of Lucien I, Yeomans, a method is disclosed and claimed for overcoming this difficulty. In brief the Yeomans method contemplates the fashioning of a chuck element rigid with the workpiece itself such that it can engage with a complemental chuck element in the lathe or boring machine in which the roughing cuts on the blank are made. In this way a positive lock,

as distinguished from a mere frictional grip, is provided between the workpiece and its support for transmitting torsion during all boring and turning operations.

The presently disclosed machine is adapted to carry out the method alluded to above and in particular to mill the closed end of the blank [0 of Fig. 2 so as to form on it an integral rib like the rib H on the completed blank of Fig. 3. In the course of this milling operation the closed end of the blank ll! is thinned so that it will be of predetermined thickness indicated by the dimension t in Fig. 3. Accurately dimensioning the thickness of metal at this point by external milling is particularly desirable in that the bottom wall of the finished shell, after completion of the turning, boring and pointing, can be completed by simply cutting off the rib II when everything else is finished. Additionally, the present machine serves to drill a recess l2 in the end of the blank to receive a lathe center. The location of this lathe center recess I2 is, in the present machine, accurately determined with respect to the longitudinal axis of the cavity within the blank, thereby insuring accuracy of wall thickness in the finished shell. It will be readily appreciated that uniform distribution of weight about its axial center line or, in other words, accuracy of wall thickness is of primary importance in artillery shells since any eccentricity of weight distribution causes them to leave their proper trajectory when fired.

General machine organization In the instant machine (Figs. 1 and 4) the workpieces ID are fed to the machine one by one by a conveyer mechanism A, the workpieces traveling in inverted vertical position in the direction of the arrow [3. An overhead transfer mechanism B picks successive blanks l0 off of the conveyer A and carries them over to the machine C where it lowers them onto suitable expansion-jaw type mandrels H! on a four-station indexing turret l5.

The present machine is designed for operation by two men. One is stationed on a platform l6 on the front of the machineand operates the conveyer A as well as the overhead transfer mechanism B seeing to it that successive blanks are properly located on the turret mandrels. The second operator is stationed on a rear platform I1 and manipulates the controls for tools which shape the blanks. The turret I5 is indexed clockwise (as viewed in Fig. 1) the blanks being loaded on it at station I. Station 2 is simply an idle station. At station 3 the second operator causes the end of the workpiece to be milled to form the rib ll. At station 4 the second operator manipulates the machine to drill the recesses l2 and when the blanks are finally returned to station I they are lifted from their supporting mandrels by the overhead transfer mechanism B and carried over to an unloader D. This unloader mechanism D is also supervised by the operator on the front platform l6 and serves to drop the machined blanks onto a suitable conveyer mechanism or the like.

Of the four main elements of the machine A, B, C and D, identified above, all but the conveyer A are mounted as a single unitary structure. For this purpose the machine is provided with a bed 18 (Fig. 4) from which rise heavy columns or side walls l9 joined at their upper ends by an arch 29. The work supporting turret I5 is journaled for rotation about a vertical axis within the confines of this structure as hereinafter more particularly described.

The'pl'atforms I6 and I1 are fixed to the uprights I9 while the unloader D is fixed to the outer side of the right hand one of these uprights. The transfer mechanism 13 is in turn supported on the arch 20.

Supply conveyer The conveyer A for supplying the blanks H) to the machine comprises anendless roller belt It led over pairs of sprockets 22 and 23 (Fig. 4). This belt 2! comprises a series of articulated sections 24 (Fig. 6) and on the pivot pins which join these sections are rollers 25 which are received in the notches or interdental spaces in the sprockets 22, 23 (Figs. 5 and 6). On each of the belt sections 24' is a rigid upright post 26 adapted loosely to receive a blank Ii telescoped down over it in inverted position. Theblanks l may be loaded onto the conveyer by hand or' in any other suitable manner.

To advance the conveyer-belt?! step-by-step' a drive mechanism is provided utilizing an electric driving motor 21 as a prime mover (Fig; 4).

This motor is connected through a speed reduction gearing 28 and a worm drive 29 with a pinion 36 meshing with a gear 3i, having" an eccen tric crank pin 32 on it. This pin is connected by a pitman 33 with a lever 34 (see also Fig. 6) rockably mounted on a shaft 35 and carrying a pawl. This pawl engages a ratchet wheel 37 pinned on the shaft 35' and to which the sprockets 23 are also pinned (Fig. A back-up pawl 38 (Fig. 6) prevents reverse rotation of the ratchet wheel 31. Each full rotation of the drive gear 3i oscillates the pitman 33 through a full stroke and each stroke of this pitman in turn causes the conveyer belt 2! to be advanced one full step or, in other words, to bring the successive one of the blanks Ill into operative relation with the transfer mechanism B.

Each advancing step of the conveyer A is initiated by a momentary closure of a push button 39 (Fig. 4) which may, incidentally, be located on the front platform iii if desired, to be convenient to the operator stationed there. Such closure of this push button 39 completesan energizing circuit for the motor 2? through suitable supply lines 46 so that its rotation is initiated. Once the gear 3! has started to revolve a cam 41., fast on it, pushes a leaf spring cam follower 42 to the left, thereby closing a normally open switch 43 to complete an alternative energizing circuit for the motor 21 from the supply lines 4&3, in shunt with that through the push button 39. The motor 21 is thus retained energized, despite subsequent release of the push button 39, until the gear 3lhas completed a full revolution at which point the cam follower 42 drops back into the recess in the cam 4| thereby permitting the switch 43 to open and stop the motor 27. Each successive advancing step of the conveyer may thus be initiated at will simply by momentarily closing the push button 39.

Overhead transfer mechanism The overhead transfer mechanism B embodies two workpiece engaging and hoisting units 44 and 45 (Fig. 4) which serve, respectively, to shift the blanks from the conveyer A to station I on the turret and from station I to the unloader D. These units are mounted on a traversing carriage 46 having wheels 41 running along rails 48 (see also Fig. 7). These rails are fixed. on a.

framework. carried by pedestals 5U rising. from the main frame arch 20.

In brief, the carriage 46 is initially positioned as in Fig. 4 with the units 44, alined respectively with a raw blank Ill. at the terminus of the conveyer A and. with amachined blank at turret station I. The blank-engaging means of the two units are lowered simultaneously, engage the respective blanks noted, and are hoistedup again, lifting these blanks. Then the carriage is traversed to the right until the unit 44 is alined with turret, station. I and the unit 45 alined with the unloader D. Thereupon the blanks are lowered tothe turret station and unloader, respectively. Having thus transferred the blanks the carriage 46 is traversed back to its initial position and this operation repeated and. continued. Thus, in each cycle of movement the transfer mechanism supplies a new blank to the machine and removes a completed one from it.

Since the units. 44, 45 are substantially identical a description of one will. sufiice for both. Upon reference to Fig. 4 it will be seen that the unit 44 includes an electromagnet 5| slidably mounted in vertical guides 52 which are bolted to the front sideofthe carriage and depend fromit. Since the blanks. 1.0 are made. of steelor'otherparamagnetic; material-they are effectually seized when, the, energized .electromagnet contacts them and are disengagedby deenergizing the mag-net; The electromagnetEt is suspended by a cable 53 leading over. a pulley 54 andanchored "to a winding, drum. 55 at the rear side of-the carriage 46 (see Fig.8.). The pulley 54 and winding drum or reel 55 are'suitably journaled on a platform 56 which extends across and is fixed tothe carriage 46.

, To revolve the winding drum .55-for reeling in and out the cable. 53, an electric driving motor 5'! (Figs. ,1 and 9) is used. This motor is connected through a speed reduction gearing 58-and worm drive 59 with a pinion 50, which inturn meshes with, a gear 6| fast on the drum- 55. Suitable control switches (not shown may, of course, be providedfor controlling the energize.- tion of the electromagnet 5!. as well as the hoisting motor 57.

Traversing of the carriage 45 along the rails 48 must be accomplished with stoppage of the units 44, 45 accurately positioned .at their respective alternative stations. A simple and rugged form of linkage-type drive (Fig. 8) has been provided for this purpose.. A firstv link 62 is pinned to an upright rock-shaft 63 (see also Figs. 9 and 1'0) which is rotatably journaled. in a suitable bearing 54 formed in one of the track way supporting pedestals 5'0. 4 'A second link 65 is pivotally' connected to the outer end of the first link 62' and to the carriage 48. It Will be observed in Fig. 8 that when the linkage 32,65 is moved from its distended position to the left (shown infull lines) to its distended position to the right (shown in dotted lines) that the carriage 45 will be traversed between its respective terminal positions in which the units44, 45 on it are alternatively located at their two stations as described above.

To effect the necessary shift of the links 6'2; 65 with respect toleach other in moving them between the two distended positions noted above a gear arrangement is utilized comprising, first of all, a stationary gear 66 coaxial with the rockshaft 63 and bolted tothe pedestal 50. Meshing with this gear 65 is a pinion 6'! rotatably journaled on an intermediate portion of the: link;

62 adapted to roll about the stationary gear 66 as the link 62 is revolved by rotation of the shaft 63. A third pinion 68 meshes with the pinion 61 and is fixed to a pin 69 that forms a pivotal connection between the links 62; 65 though being fixed to the latter. Thus, as the shaft 63 is rocked in a counterclockwise direction (as viewed in Fig. 8) the link 62 will be swung correspondingly from the full line position to the dot-dash line position there shown. In the course of such movement of the link 62, the pinion 61 rolls around the stationary gear 66 and as a consequence rotates the pinion 68. Such rotation of the pinion 68 swings the outer link 65, which is connected to it through the pin 69, to the dotdash position shown so that the linkage 62, 65, is partially collapsed. As the rotation of the shaft 63 continues in the direction noted the links 62, 65 continue to move toward each other until the linkage is completely collapsed after the link 62 has moved through 90. Thereafter the linkage begins to distend on the opposite or right hand side, as viewed in Fig. 8, finally reaching the fully distended position shown in dotted lines.

Power actuated means, comprising an electric traversing motor 10 (Fig. 8) is used for oscillating the rock-shaft 63 to move the linkage as described. To this end the motor 16 is connected through a speed reduction gearing H and a worm drive 12 with a pinion 13 (see also Fig. 9) meshing with a gear 14 pinned to the lower end of the shaft 63. The motor 16 is reversible and is energized from supply lines l5, 76 (Fig. 8). The supply line 18 is permanently connected to one motor terminal 11. When the line 15 is connected to terminal 18 the motor rotates in one direction to revolve a shaft 63 clockwise, and when the line 15 is connected to the other terminal 19 the motor revolves in the opposite direction to turn the shaft 63 in a counterclockwise direction. A reversing switch 80 serves to connect the line 15 to the terminals l8, "19 when in its forward and reversing positions, respectively and to open-circuit the motor, thereby stopping the same, when in its neutral position shown. A limit switch 8| is interposed in the leads between the reversing switch 80 and the motor 18, this limit switch being arranged for actuation by a dog 62 on the link 62. When the link 62 is swung fully to the left, as shown in full lines in Fig. 8, it causes the switch ill to open-circuit the lead from the reversing switch 80 to the terminal 19 though leaving the lead to the terminal 76 closed. Conversely, when the link 62 is swung fully to the right it causes the switch 8| to open the lead to the terminal '18 while leaving the lead to the terminal [9 closed.

A prime advantage of the traversing mechanism for the carriage 46 described above is the precision of location of the carriage at the respective ends of its path of travel despite inaccuracies in, or lack of, full distention of the linkage 62, 65. In this connection it should be noted that when the linkage 62, 65 is substantially fully distended, comparatively large angular movements, or inaccuracies in position of the rockshaft 63 will result in but small corresponding displacements of the end of the link 65 and hence of the carriage 46. As a result even though the limit switch 8| should not stop the linkage in precisely its fully distended position, there will be very little inaccuracy in the location of the carriage.

Turret structure The turret, designated generally at l5, ior the machine C comprises an upright hollow spindle 83, the upper and lower portions of which are shown respectively in Figs. 15 and 16. The lower end of this spindle 83 is steadied against side play in a suitable sleeve bearing structure 84 bolted to the machine bed l8 while the weight of the turret is hung on roller bearings 85 running on the upper end of a sleeve 85 bolted to the webbed central portion of the arch 26. As shown in Fig. 15 a tubular extension 86, for the upper end of the spindle 83, is fixed to it by cap screws 81, the axial bores within the spindle 83 and extension 86, communicating with each other and serving as a supply passage for a pressure fluid system hereinafter described.

Rigid with the upper portion of the spindle 83 is a horizontal disk shaped head casting 88 (Figs. 4, 7, 11, 15 and 16). In this head 88 are four holes 89, equidistantly spaced about the vertical axis of the spindle 83, and in which are loosely received the workpieces H! at the four stations for the turret. On this head 86 are suitable clamping mechanisms hereinafter described for gripping the upper ends of the blanks it] which project through the holes 89. The turret also comprises .the four mandrels (6, previously mentioned, located beneath and projecting into the holes 89 in the head 88 and on which the respective blanks l6 are carried.

Indexing movement of the turrent I5 is accomplished by means of a drive motor 98 operating through a pawl and ratchet drive substantially like that heretofore described for the conveyer A (see Figs. 14 and 15 and also Figs. 1 and '7). The motor 96 is drivingly connected through a speed reduction gearing 9| and a worm drive 92 with a pinion 93 which in turn meshes with the gear 94. This latter gear carries an eccentric crank pin 95 to which is pivotally connected a pitman 96, pivoted at its opposite end to a rocker link 9'! loosely journaled on the upper end of the turret spindle extension 86. On this rocker link 97 is a driving pawl 98 engageable with a four-notch ratchet wheel 99 fast on the spindle extension 86. A spring pressed back-up pawl I60 prevents reverse rotation of the ratchet wheel. Each stroke of the pitman 96 thus causes the ratchet mechanism to advance the turret l5 rotatably through degrees. A switch IOI, operated by a cam I62 fixed to the ratchet wheel 99, operates in the manner of the switch 13 heretofore described for the conveyer A (cf. Fig. 4) to retain the motor 96 in operation during the full completion of each indexing step and then automatically stops the same.

To aid in locating the turret l5 precisely in its successive indexed positions a stop I63 (Figs. 4, 11 and 14) is spring urged toward the turret to engage one of the four complemental notches I04 located at 90 degree intervals about the periphery of the head 68. A solenoid I05 acts, upon energization thereof, to retract the stop plunger I63 to free the turret for rotation to its next successive position. This solenoid is arranged to be energized upon each initiation of the operation of the indexing drive motor 96 through a suitable common energizing circuit (not shown) for the solenoid and motor.

Turning now to the details of the turret mandrels 14, each of them serves to locate a workpiece telescoped down over it and, being of the expansion-jaw type, interiorly grip it. These four mandrels are carried respectively on the outer ends .of four box shaped supports I 08, spaced at intervals of 90 degrees about the turret axis, and bolted to complemental flat pads or faces on the spindle 83. Since all four of the mandrels are of identical construction, a de-' scription of one will suffice for all. Referring to Fig. 16, it will be observed that the mandrel I4 there detailed comprises a spindle I06 rotatably journaled in a sleeve bearing I 01 received in a supporting bracket I08 bolted to the outer end of the box support I08. Fixed to the upper end of the spindle I06 is a spindle extension I99 having a longitudinal axial bore III]. Opening laterally from the bore III! is a lower set of three slots III equidistantly spaced about the mandrel axis (Fig. 17) and at the upper end of the mandrel is a similar set of slots I I2 (Fig. 16). In each of these slots is received :a radially movable clamping shoe I I4 which is, in general, thrust radially outward to grip the encircling side walls of the blank III. Each of the shoes H4 is yieldably urged inward by leaf springs II3 (Fig. 16), which are riveted at their inner ends to the spindle extension I69 and arranged with their outer ends received in complemental notches in the shoes I I4.

To actuate the shoes H4 radially outward into engagement with the blank III, a plunger H5 is arranged to slide axially in the spindle bore H and carries at its opposite ends wedges I I6 and II! which bear against complementally tapered faces on the shoes H4. The lower wedge II! is pinned to the plunger I I5, while the upper wedge I I has a lost motion connection with the plunger I through a pin I18 and a compression spring H9. The upper end of this pin H8 is fixed t0 the wedge, while its lower end carries a collar I20 slidable in the interior of the plunger II 5 and against which the spring II9 bears. Thus when the wedge I I1 is drawn downward it forces the lower shoes II4 outward. At the same time the upper wedge H6 is yieldably drawn downward so that it forces the upper shoes II4 outward. This yieldable connection between the wedges I I5, I I1 permits some differences in movement of them to accommodate any inequalities in the shape of the cavities within the workpieces.

In order to pull the wedges IIB, II'I downward into shoe-projecting position, a weight I2I is utilized (Fig. 16). This weight is generally cupshaped in form and in the machine shown, may be of, say, four hundred and fifty to five hundred pounds. It is attached to the lower end portion of a stem of rod I22, slidable in an axial bore I23 in the spindle I06 and attached at its upper end to the wedge II'I. It will be observed that the lower portion of the bracket I08, in which the lower end of the spindle IDS is journaled by a sleeve bearing I24, forms an annular housing I25 encircling and protecting the Weight IZI.

With the parts arranged as described, the weight I2! normally biases the wedges IIB, II'I downward so that the shoes II4 are thrust outward into frictional engagement with an encircling blank II To free the blank from the mandrel it is necessary to lift the weight I2I and thrust the stem I22 upward. A hydraulic mechanism is provided for this purpose at the turret station I (Figs. 4 and 7). Thus a hydraulic cylinder I25 is located in a suitable recess in a machine bed I8 so that its plunger I26 will be alined with the lower end of the stem I22 of any particular one of the mandrels positioned above and stem so as to release the mandrel supplemental clamping mechanisms eters.

it. Upon admitting pressure fluid through suitable supply lines (not shown) to the cylinder I25 at the lower end of the plunger I26, the latter is thrust upward and thereby lifts the weight clamping shoes II4.

From the foregoing it will be seen that, in general, the mandrel clamps are such that each of them can "be successively disengaged and reapplied through manipulation of the single hydraulic mechanism" I25, I26, at station I where the blanks I0 are both loaded and unloaded. At all. other stations the mandrel clamp shoes I14 remain actuated, but since a biasing weight is provided for that purpose, it is unnecessary to have any hydraulic actuating mechanism or the like for these mandrel clamps on the revolving turret itself. v

Supplemental to the mandrel or interior clamp shoes I I4 described above, means is provided for exteriorly gripping the blanks II) on the mandrels I4 at certain stations, particularly when the blanks are being milled at station 3. Such supplemental gripping is necessary during the milling since each of the mandrels is freely revolvable in its supporting bearings I01, I24, described above and the blanks must be held nonrotatably during the milling of the transverse rib I I on them. The supplemental clamping means is located on the upper turret head 88 (Fig. 11) and is of such character as to accommodate itself to variations in diameter of blanks I0 carried by the mandrels.

In the illustrated construction, each of the I27 comprises a pair of 7 generally floatingly mounted jaws I28, I29. 1 The jaw I28 has a workpiece engaging lug I38 on it, While the jaw I29 has a pair of such lugs I34, I32, so that the jaws grip the workpiece at three spaced points about its periphery. At one end, the jaws I28, I 29 are connected by a pivot pin I33 journaled in a block I34 slidable in a T-slot I35 (Fig. 13) fashioned in a second block I33 screwed to the head 88. The slot I35 extends generally radially of the blank II! so that the pair of jaws can move bodily, by shifting of the block I34 in the slot I35, to accommodate blanks of different diam- To draw the free ends of the jaws I28, I29 together into clamping engagment with the work, a hydraulic piston I37 is provided in a cylinder I38 (Fig. 11). The piston is connected to the jaw I29, while the cylinder is connected to the jaw I28, and a compression spring I39 in the lower portion of the cylinder normally urges the jaws apart. To draw the jaws together, pressure fluid is supplied to the opposite face of the piston I37 through a supply line I453, thereby forcing the piston down into the cylinder and drawing the jaws together.

With the floating clamp jaw arrangement described above, it is necessary to provide some means for holding the jaws I28, I29 against movement with respect to the head 88 after they have been brought into gripping engagementwith the Work. For this purpose clamping feet MI are arranged to span the gap between the ends of the clamping jaws (Fig. 11) These feet I4I are fixed to a stem I42 of a piston I43 slidable in a hydraulic cylinder I44 (Fig. 12.) A helical compression spring I45 normally urges the piston I43 upward so as to release the feet I4I. To draw the feet down into clamping position against the jaws I28, I29, pressure fluid is admitted to the upper face of the piston I43 through a fluid supply line I46.

It will be understood from the foregoing that each of the supplemental clamping mechanisms I21 for the several stations on the turret are identical. In each of these clamping mechanisms pressure fiuid for the cylinders I38 and I44 is supplied from some suitable source such as an air compressor (not shown) connected to the hollow interior I41 of the main turret spindle 83 (Fig. 15) through a conduit I48 and an axial bore I49 in the spindle extension 86. This pressure fiuid is led off to the various clamp actuating cylinders through radial passages I50 (see also Fig. 11) individually controlled by manually operable three-Way valves I5I. These valves can, in the usual manner, be turned either to supply fluid to their respective cylinders, to shut off the flow of such fluid, or to bleed such fluid to atmosphere from the controlled cylinders. With the machine disclosed, the operator on platform I1 at the rear of the machine (see Fig. 1) ordinarily reaches in and manipulates the valves I5I to clamp the successive blanks at idle station 2 so that they will be ready for milling at station 3. Then upon the completion of the milling, he again manipulates the valves to cause release of the supplemental clamps so that the mandrels I4 can be freely revolved, as herein after described, at station 4 for drilling the lathe center recesses I2 in the ends of the blanks.

Milling workpiece At station 3, three milling cutters I52 ,I53, I54 are fed across the exposed end of each blank 10 located at such station to reduce its end wall to predetermined thickness and to form the rib II on it, heretofore described (Figs. 18, 19, 20 and 21). The cutters are keyed coaxially to a common shaft or arbor I55 (Fig. 20) and the center cutter I54 in the group is of somewhat lesser diameter than the other two so that as they are fed across the end of the workpiece, the center cutter will mill the top of the rib II while the other cutters I52, I53, which are of equal diameter, will mill the adjacent portions of the blank lying on each side of the rib.

The drive mechanism for the arbor I55 terminates at two pinions I55, I51, secured to respective opposite ends of the same (Fig. 20) so as to equalize the torsional strain on the shaft. To drive these pinions in unison from a single drive motor I58 (Figs. 18 and 19) the motor is connected through a pinion I53 with a gear I51." which is fast on a short shaft having a pinion I59 on its outer end that in turn meshes with a gear I60. This gear IE is fixed on a shaft II having a pinion I62 keyed on its opposite end (Fig. 21). This pinion I62 in turn meshes with a gear I63 fixed on a transverse shaft I64 to which are fixed pinions I55, I66 meshing respectively with the pinions I56, I51 on the arbor I55. The drive motor I53, together with the gearing just described, which comprises the connection to the arbor I55, are mounted on the underside of a slide I51 in which the cutter arbor I55 is also journaled (Figs. 18, 19 and 20).

Means is provided to support the slide I61 for traversing movement in a direction radial of the turret in order to feed the milling cutters I52, I53, I55, generally diametrically across the exposed end of one of the blanks ID at turret station 3. To this end, elongated guides I68 of inverted T-shape cross section (Figs. 18 and 20) are fashioned on the arch 29, these guides being received in complemental guideways I69 in the upper face of the slide I61. Gibs I10 secure the slide in place.

To feed the cutter slide I51 along the guides 158 an electric feed motor I1I is used as a prime mover (Fig. 18). This feed motor is connected through a speed reduction gearing I12, a worm drive I13 and a second speed reduction gearing I14 with a shaft I15 journaled in the arch 20 above the slide. This shaft I15 is in turn connected through a spiral gear I16 (see also Fig. 19) with a shaft I11, which parallels the path of movement for the slide I61. The shaft I11 is connected through gears I13 with a feed screw I19, which is rotatably journaled in the arch or superstructure 20 though restrained against endwise movement. A traveling nut I19 fixed on the slide I61 is threaded on the screw I13. Thus, as the feed motor I1I rotates the screw I18, the slide IE1 is traversed along its ways I58. Both the cutter drive motor I58 and feed motor I1I are controlled through suitable manual switches (not shown) by the operator stationed at the rear of the machine.

An end wall on the blank II] of accurately determined thickness t (Fig. 3) is thus formed since the active edges of the milling cutters are accurately located at the fixed distance t above the upper ends or noses of the mandrels I4 and the latter abut against the inner ends of the cavities in the blanks.

Drilling lathe center recess At station 4 the lathe center recess I2, heretofore noted, is drilled in the exposed end of each of the blanks I0 presented at this station. As a means of insuring concentricity of the walls in the finished shell it is of prime importance that this lathe center recess I2 should be concentric with the cavity in the interior of the blank. In order to make sure of this relation, the lathe center recess I2 is formed by rotating the mandrel I4 which carries the blank and shifting a nonrotatable drill or counterbore bit into engagement with the end of the blank to fashion the recess.

In the illustrative construction (see Fig. 16) rotation of the mandrels I4 presented at station 4 is accomplished by means of an electric drive motor I80. This motor is connected through suitable gearing I8I with an axially shiftable clutch driving element I82. A complemental clutch driven element I83 is fixed to a gear I84 journaled on the bracket I98 and meshing with a gear I85 concentric with the mandrel spindle I06 and fixed to the same. By shifting the clutch driver I82 upward, by means of a shifter fork I86 operated by hand lever I81, the clutch elements are engaged to connect the mandrel spindle I05 in driven relation with the motor I39 for rotation of the blank II) at station 4. It will be observed that the connections from the clutch driven element on over to the mandrel spindle are duplicated for each mandrel (see Fig. '1) but that only one driving motor 89, together with the rest of its connections, need be provided for rotating the successive mandrels presented to it.

After the operator has started the motor 80 and drawn up the lever I81 to engage the clutch I82, I83 to set the mandrel I4 spinning at station 4, he brings a counterbore bit or drill I88 down into engagement with the blank Ii] (Fig. 15). The bit N38 is fixed to the lower end of a plunger I89 arranged to be moved axially by means of a hand lever I90 (Fig. '1) through the trolled by a manually operated reversing switch medium of a cross shaft I9I and rack and pinion I92 (Fig. 15). The lathe centerr'ecess I2 isthus drilled in accurate alinement with the longitudinal center line of the cavity in the workpiece since the axis of rotation of the workpiece is co-. incident with the center line of its interior cavity by virtue of its mounting on the spinning mandrel. The frictional grip of the mandrel on the workpiece is, of course, sufficient to prevent relative rotation between the workpiece and mandrel during the drilling operation.

To prevent inadvertent indexing of the turret I while the drill bit I83 is still in engagement with the work a switch I90 (Fig. 14) is arranged to be held open by the handle 599 except when the latter is positioned for retraction of the bit. This switch is interposed in the circuit of the indexing motor 90 and retains the same open-circuited so long as the switch is open.

Unloader The milled and drilled blanks it} on the turret I5 are finally returned to station 1 after four successive indexing movements of the turret. Upon returning to this station they are, in brief, released from the mandrel I4 presented at the station, lifted from it and carried by the overhead transfer mechanism B to the unloader D, which dumps them successively onto a suitable conveyer indicated at I93 (Fig. 22).

To release the finished blanks I 9 at station I, the hydraulic plunger I26 is thrust upward, as heretofore described, thus lifting the weight I2! and stem I22 of the particular mandrel presented to it (see Fig. 16) thereby releasing the grip of the mandrel shoes M4 on the blank. The overhead conveyer mechanism B is. positioned as shown in Fig. 4 with the unit 35 above turret station I. Then the electromagnet of the unit 45 is lowered, energized to engageithe finished blank, and rehoisted after which the transfer carriage 45 is traversed to the'rlght until the blank I9 is properly alined to be received in the unloader mechanism D.

The unloader mechanism D comprises (Fig. 2) v a framework I94 bolted to the outer side of one of the machine columns. A workpiece-receiving electromagnet I95 of jaw form is pivotally supported on this framework by a shaft 96 for rocking movement from the upright "position shown in full lines in Fig. 22 to the horizontal position shown in dot-dash lines. To rock the unloader magnet I95 between the positions noted, a reversible electric drive motor I9! is utilized (Figs. 22, 23 and see also Figs. 1 and 4). This motor is connected with a gear I9 9 (journaled on the rock shaft I96 and bolted to the magnet I95) through a speed-reduction gearing I99, a wormdrive 290 and a pinion 29! (Fig. 24) meshing with a gear 202 fixed on an intermediate shaft 293, which also has pinned to it pinions 294 meshing with the gears I98.

The energization of the unloader electromagnet I95 may be controlled through the medium of a suitable manual switch (not shown) manipulated by the operator at the front of the machine. When one of the blanks I9 is lowered into position in the unloaders magnet I95, the latter'is energized to seize the blank and the electromagnet of the hoisting unit 45 deenergized to release it. The unloader electromagnet I95 continues to hold the blank until it is swung down into posi tion over the conveyor I93, whereupon the magnet is deenergized to drop the blank.

Operation of the unloader motor I9! is con- 295 (Fig. 22) movable from a neutral or N position shown, in which the motor is deenergizedto either raising or lowering positions R or L in which the motor is respectively energized. for

raising and lowering the rockably .mounted magnet I 95. Electrical interlocks are also provided for insuring proper location of the blank I'D in theunloader and for stopping the motor I91 at the end of each cycle of movement. For the former purpose a switch 296 is interposed in the lead :29? from the lowering contact of the main switch 265, the switch 206 being closed by :a dog 298, located to be actuated a blank I0 in place on the magnet, so that the motor I91 cannot be energized to lower the unloader magnet I95 until the blank is properly located. For the cycle control, a double switch 299 is interposed in the motor leads 201, 2H] so as to open-circuit one or the other. This switch 209 is actuated by a pair of pins 2, 212 on one of the gears I99. Thus when the parts are positioned as shown in Fig. 22 the pin 2II shifts the switch 299 to open the motor lead 2H] and thus prevent further raising of the magnet, although leaving the other lead 291 closed. 'Then'when the lowering contact L of the manual switch 295 is closed the'mo'tor is energized to lower the magnet I95 until the pin 2I2 shifts the switch 209, where upon lead 2'07 is opened,-stop-ping the motor, and lead 2 I9 closed, preparatory to a subsequent raising of the magnet when the manual switch is shifted for that purpose.

Brief rsume' of operation machine. The operator on the front platform I6 presses the push button 39 each time that he wishes the conveyer A to advance a step in order topresent another blank. Then this same operator lowers the pick-up electromagnets of the units 44, of the overhead transfer mechanism B, with the latters carriage 45 positioned at the left hand extremity of its path of travel, as shown in Fig. 4. He causes these electromagnets to be energized so that they seize respectively the last blank in the row on the top of the conveyer A and the finished or machined blank located at station I of the machine turret I 5. Incidentally, this latter blank has, at such time, been disengaged from its mandrel by means of the hydraulic plunger I29 which .is thrust upward to lift the weight 1 2| and thereby cause the mandrel gripping shoes H4 to release. Next, the operator causes the pick-up electromagnets to be .hoisted and traverses the carriage 46 of the presented to it and deenergizes the transfer mechanism electromagnets. These latter electromnagnets are then rehoisted and the carriage 46 traversed back to'its initialposition preparatory to its next cycle of operation. To discharge the blank from the unloader D the operator shifts the manual switch 285 (Fig. 22) to its L or lowering position, whereupon the unloader motor I9! is energized to rock the electrom-agnet 195 down into its lowered position (shown in dot-dash lines in Fig. 22). Finally, the electromagnet 195 is deenergized to drop the finished blank onto the conveyer I33.

While the operator at the front of the machine manipulates the loading and unloadin mechanisms for fresh and finished blanks, as described above, the second operator on the platform I! at the rear of the machine operates the various controls of the machine for indexing the turret l and effecting the desired milling and drilling operations. Thus, after the first operator at the front of the machine has positioned a fresh blank on one of the mandrels l4 presented at station I. he lowers the hydraulic piston I26 50 that the weight I2! drops down and causes the mandrel shoes ll l to grip the blank. Then the second operator at the rear of the machine takes over. He energizes the turret indexing motor 90 (Fig. 14) to index the turret through one step, i. e., 90, to move the fresh blank to station 2. While the blank is in station 2, the operator manipulates the corresponding set of control valves I51 (Fig. 11) to cause the supplemental clamping means I21 on the turret head 88 to grip the blank at station 2 and hold it against rotation. Next, the second operator starts the drive and feed motors I58 and ill for the milling cutters I52, I54 (Fig. 18), so that the latter are fed across the end of the next preceding fresh clamped blank located at station 3. While these milling cutters are moving across the exposed end of the blank to mill it to predetermined thickness and fashion the rib H, the operator turns to station 4, where he drills the lathe center recess H! in the milled blank located there. For the latter purpose the second operator manipulates the valves l5! to disengage the supplemental clamping mechanism I21 on the blank located at station 4 (Fig. 11). Then he sets the mandrel drive motor I80 in operation (Fig. 16), and swings the hand lever It! to engage the clutch I82, I83 to revolve the mandrel and blank at station 4. Thereafter he grasps the drill feed lever I90 (Figs. 14 and 15) and swings it to push the drill bit I88 down into engagement with the top of the revolving workpiece.

Upon completing the drilling operation noted above, the operator disengages the clutch I82, 83 to stop the rotation of the mandrel at station 4. By that time the milling operation at station 3 is complete and he reverses the feed for the milling cutters, moving them back to their initial position. The respective machining operations at stations 3 and 4 are thus complete so that the second operator is ready to index the turrent l5 through another step, thereby moving the completed or finished blank from station 4 back to station I, where the first operator unloads it, as described above.

From the foregoing, it will be seen that a series of even large and heavy work blanks can be handled and machined expeditiously with the apparatus described, and through the services of only two operators. The various operations which these workmen respectively control are so correlated with each other, and the parts of the machine so located, that each man can efficiently supervise the operation of several different machine elements.

I claim as my invention:

1. In a machine tool, the combination of a turret mounted for rotational indexing movement, a plurality of upright expansion-jaw type mandrels rotatably mounted on said turret at spaced points about its axis of rotation, power actuated means for indexing said turret to bring said mandrels successively to a series of stations, a first metal removing tool at one of said stations, means on said turret for releasably exteriorly clamping individually tubular workpiece blanks telescoped over the respective mandrels to hold them against rotation, power actuated means for feeding said first tool with respect to a blank on a mandrel located at one of said stations to efiect a metal removing operation on said blank with the latter clamped by its clamping means, a second metal removing tool located at a second station, and power actuated means for revolving successive ones of the mandrels at said second station with said second tool in engagement with the blanks on them and with said clamping means released.

2. In a machine tool, the combination of a revolubly mounted expansion-jaw type of mandrel shaped to receive and interiorly grip a generally tubular metal blank telescoped over it, a first metal removing tool, means for releasably exteriorly clamping a blank on the mandrel to hold it against rotation, power actuated means for effecting a relative feeding motion between the mandrel and said first tool with the blank clamped by said clamping means, a second metal removing tool, and power actuated means for revolving said mandrel with said second tool in engagement with a blank on it and said clamping means released.

3. In a machine tool, the combination of a turret comprising a spindle rotatably indexable about a vertical axis, a generally disk shaped head fixed to said spindle and having apertures therein at spaced points about the spindle, supporting means rigid with the spindle and projecting laterally therefrom in spaced relation beneath said head, a plurality of upright mandrels revolubly mounted on said supporting means and projecting upwardly through said apertures to receive generally tubular metal blanks telescoped down over the same through said apertures, said mandrels including means for releasably gripping interiorly the blanks telescoped over them, and means on said head including a pair of clamping jaws arranged at each of said apertures to embrace and releasably grip the exterior of a blank on the mandrel projecting therethrough.

4. In a machine tool, the combination of a turret comprising a spindle rotatably indexable about a vertical axis, a generally disk shaped head fixed to said spindle and having apertures therein at spaced points about the spindle, supporting means rigid with the spindle and projecting laterally therefrom in spaced relation beneath said head, a plurality of upright mandrels revolubly mounted on said supporting means and projecting upwardly through said apertures to receive generally tubular metal blanks telescoped down over the same through said apertures, said mandrels including means for releasably gripping interiorly the blanks telescoped over them, means on said head including a pair of clamping jaws arranged at each of said apertures to embrace and releasably grip the exterior of a blank on the mandrel projecting therethrough, means including a first metal removing tool mounted about said turret for machining successive blanks at one station in the indexing movement of the turret with the blank held against rotation by its associated pair of clamping jaws, power actuated means for revolving said mandrels when said clamping jaws are released, and means including a metal removing tool at a second station for engagement with successive blanks presented thereto in the indexing movement of said turret for machining of the same upon rotation of their mandrels.

5. In a machine tool, the combination of a turret comprising a spindle rotatably indexable about a vertical axis, a generally disk shaped head fixed to said spindle and having apertures therein at spaced points about the spindle, supporting means rigid with the spindle and projecting laterally therefrom in spaced relation beneath said head, a plurality of upright mandrels revolubly mounted on said supporting means and projecting upwardly through said apertures to receive generally cup shaped metal blanks telescoped down over the same through said apertures, said mandrels including means for releasably gripping interiorly the blanks telescoped over them, means on said head including a pair of clamping jaws arranged at each of said apertures to embrace and releasably grip the exterior of a blank on the mandrel projecting therethrough with the end face of the blank exposed, means including a milling cutter mounted for horizontal feeding motion above said turret for surfacing the ends of successive blanks at one station in the indexing movement of the turret with the blanks held. against rotation by their associated pair of clamping jaws, power actuated means for revolving said mandrels when said clamping jaws are released, and means including a nonrotatable drill arranged to be fed axially against the ends of the blanks at a subsequent station for drilling the ends of successive blanks presented thereto in the indexing movement of said turret upon rotation of such blanks to the last mentioned station.

6. In a machine tool, the combination of a rotatably indexable turret comprising a rotatable spindle with a longitudinal bore and having a head on it with a plurality of apertures therein distributed about the axis of turret rotation, a plurality of revoluble mandrels on the turret pro jecting through respective ones of said apertures adapted to receive generally tubular workpieces telescoped over the mandrels through said apertures, said mandrels including means for releasably interiorly gripping the workpieces on them, supplemental clamping means for each of the workpieces on the several mandrels, each of the complemental clamping means comprising a pair of jaws fioatingly mounted on said head to exteriorly grip a workpiece on the associated mandrel and a hydraulic actuator for the pair of jaws, and means for supplying pressure fluid to said actuators through said bore in the turret spindle.

'7. In a machine tool, the combination of a head having an aperture therein, a mandrel projecting through said aperture and adapted to receive a generally tubular workpiece telescoped over the same, a pair of jaws slidabie along the surface of said head adjacent said aperture and arranged to embrace the exterior of a workpiece on the mandrel, means on said head forming a guide- 7 way extending toward said aperture in a direction radial of the mandrel, a supporting block slidable in said guideway and to which one end of each of said jaws is pivotally connected, means for drawing together the other ends O Said, jaws to bring them into gripping engagement with the blank, a clampingfoot overlying said other ends of said jaws, and means for urging said clamping foot toward said head to clamp said other ends of said jaws against the same and thereby restrain them against bodily movement. a

8. In a machine tool, a mandrel adapted to receive a generally tubular workpiece telescoped over the same, a pair of clamping jaws arranged to embrace the exterior of a workpiece on the mandrel, means forming a floating support for said jaws to permit bodily movement thereof in order to accommodate variations in the diameter of the successive blanks on the mandrel, said last mentioned means comprising a support guided for movement radially toward and away from the axis of the mandrel and to which'said jaws are pivotally connected at one end, and means for drawing together the other ends of said jaws to bring them into gripping engagement with the blank.

9. In a machine tool, a mandrel adapted to receive a generally tubular workpiece telescoped over the same, a pair of clamping jaws arranged to embrace the exterior of a workpiece on the mandrel, means forming a floating support for said jaws to permit bodily movement thereof in order to accommodate variations in the diameter of the successive blanks on the mandrel, said last mentioned means comprising-a support guided for movement radially towardandaway from the axis of the mandrel and to which saidjaws are pivotally connected at oneend', means for drawing together the other ends of; said jawsto bring them into gripping engagement with the blank, and means for releasably locking said jaws and said first mentioned means against bodily movement relatively to the mandrel.

10. In a machine of the type described, the combination with work supporting means for rigidly holding a cup shaped metal workpiece with the face of its closed end exposed, of a gang of three rotary milling cutters revoluble about a common axis and comprising a pair of cutters of equal diameter with a third cutter of different diameter interposed between them, and meansfor feeding said gang'of cutters generally diametrically across said exposed-end face of a workpiece on the supporting means to surface said face and form an integral transverse coupling elementthereon. 4

11. In amachine of the type described, for milling to a selected thickness the closed'endof a cup shaped metal blank, the combination of an expansion-jaw type mandrel adapted to be inserted in and to grip interiorly a cup shaped metal blank with the free end of the mandrel abutting against the bottom of the cavity in the blank, a milling cutter, and means for feeding said cutter and mandrel relative to each other in a path transverse to the mandrel axis and with the cutter located a preselected fixed distance from said free end or"- the mandrel equal to a desired finished thiekness'of the end of the blank.

12. In a machine of the type described-for machining to a selected thickness the closedzend of a cup shaped metal blank, the combination 

